CN103917431B - Hydraulic pressure control device and possess the vehicle for construction of this hydraulic pressure control device - Google Patents
Hydraulic pressure control device and possess the vehicle for construction of this hydraulic pressure control device Download PDFInfo
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- CN103917431B CN103917431B CN201280054904.1A CN201280054904A CN103917431B CN 103917431 B CN103917431 B CN 103917431B CN 201280054904 A CN201280054904 A CN 201280054904A CN 103917431 B CN103917431 B CN 103917431B
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- working oil
- control cock
- oil
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Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62D—MOTOR VEHICLES; TRAILERS
- B62D5/00—Power-assisted or power-driven steering
- B62D5/06—Power-assisted or power-driven steering fluid, i.e. using a pressurised fluid for most or all the force required for steering a vehicle
- B62D5/07—Supply of pressurised fluid for steering also supplying other consumers ; control thereof
- B62D5/075—Supply of pressurised fluid for steering also supplying other consumers ; control thereof using priority valves
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62D—MOTOR VEHICLES; TRAILERS
- B62D5/00—Power-assisted or power-driven steering
- B62D5/06—Power-assisted or power-driven steering fluid, i.e. using a pressurised fluid for most or all the force required for steering a vehicle
- B62D5/065—Power-assisted or power-driven steering fluid, i.e. using a pressurised fluid for most or all the force required for steering a vehicle characterised by specially adapted means for varying pressurised fluid supply based on need, e.g. on-demand, variable assist
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62D—MOTOR VEHICLES; TRAILERS
- B62D5/00—Power-assisted or power-driven steering
- B62D5/06—Power-assisted or power-driven steering fluid, i.e. using a pressurised fluid for most or all the force required for steering a vehicle
- B62D5/07—Supply of pressurised fluid for steering also supplying other consumers ; control thereof
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- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/08—Superstructures; Supports for superstructures
- E02F9/0841—Articulated frame, i.e. having at least one pivot point between two travelling gear units
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- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/225—Control of steering, e.g. for hydraulic motors driving the vehicle tracks
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- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2278—Hydraulic circuits
- E02F9/2282—Systems using center bypass type changeover valves
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2278—Hydraulic circuits
- E02F9/2285—Pilot-operated systems
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- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2278—Hydraulic circuits
- E02F9/2296—Systems with a variable displacement pump
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
- F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
- F15B11/042—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in"
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
- F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
- F15B11/162—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for giving priority to particular servomotors or users
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
- F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
- F15B11/167—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load using pilot pressure to sense the demand
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/35—Directional control combined with flow control
- F15B2211/351—Flow control by regulating means in feed line, i.e. meter-in control
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/455—Control of flow in the feed line, i.e. meter-in control
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mining & Mineral Resources (AREA)
- Civil Engineering (AREA)
- Structural Engineering (AREA)
- Mechanical Engineering (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Chemical & Material Sciences (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Fluid-Pressure Circuits (AREA)
- Operation Control Of Excavators (AREA)
- Power Steering Mechanism (AREA)
Abstract
Hydraulic pressure control device (10), possesses: the oil pressure pump (30) be connected side by side with cylinder (22) with steering cylinder (18L, 18R) and jib; Control turning to of the direction of the working oil flowed in steering cylinder (18L, 18R) and use control cock (34); With on center position, oil pressure pump (30) is connected with tank (48), deviation post controls flow into the jib control cock (44) of jib with the direction of the working oil in cylinder (22).In addition, hydraulic pressure control device (10) possesses: according to turning to the inlet restriction formula compensator (33) increasing the flow flowed into wherein by the front and back pressure in the variable restrictor portion (37) of control cock (34); With according to flow into steering cylinder (18L, 18R) working oil pressure increase and reduce the flow flowed in jib control cock (44), thus the oil pressure of course changing control loop (31) is remained on the discharge formula compensator (42) of the pressure preset.
Description
Technical field
The present invention relates to possess the oil pressure pump be connected side by side with steering hardware and operating apparatus actr, the flow controlling to flow in described steering hardware turn to control cock and control the flow flowed in described operating apparatus actr actr control cock hydraulic pressure control device and possess the vehicle for construction of this hydraulic pressure control device.
Background technology
The construction vehicle of the wheeled of wheel type loader etc. possesses and turns to actr, by turning to actr to supply working oil to this, can change the direct of travel of vehicle body with this.Actr is turned to pass through to turn to and be connected with oil pressure pump by control cock.Turn to the direction switching the working oil flowed in steering hardware by control cock according to the operation of handle, turn to the direction of the working oil in actr to make to turn to actr to stretch with this by switching to flow into or shrink and change the direct of travel of construction vehicle.
Again, construction vehicle possesses operating apparatus cylinder, by supplying working oil to this operating apparatus cylinder, can realize the lifting driving etc. of the operating apparatus of scraper bowl etc. with this.Operating apparatus cylinder is connected with oil pressure pump by operating apparatus control cock.Operating apparatus control cock switches the direction of the working oil flowed in operating apparatus according to the operation of control lever, and the direction being flowed into the working oil in operating apparatus cylinder by switching is made operating apparatus rise with this or declines.
This operating apparatus control cock uses the flow-controlling gate of open center (centeropen) type, and on center position, oil pressure pump is connected by restriction with tank (tank).In oil pressure pump, adopt the oil pressure pump of variable capacity type, oil pressure pump is according to its discharge rate of the Stress control produced on the upstream side of this restriction.
These turn to and are connected side by side with pressure-gradient control valve (priorityvalve) by control cock and operating apparatus control cock, and be connected with oil pressure pump further by this pressure-gradient control valve, pressure-gradient control valve preferentially supplies with control cock side the working fluid (such as with reference to patent documentation 1) coming from oil pressure pump to turning to when the driving of steering hardware.
Prior art document:
Patent documentation:
Patent documentation 1: Japanese Unexamined Patent Publication 2006-27351 publication.
Summary of the invention
The problem that invention will solve:
Fig. 5 is the birds-eye view that existing wheel type loader 1A, 1B are shown.Fig. 5 (a) is that Fig. 5 (b) is the figure of the wheel type loader 1B when making pressure-gradient control valve 9 and operating apparatus control cock 8 be formed integrally at the figure making pressure-gradient control valve 9 with the wheel type loader 1A turned to when forming one by control cock 7.In wheel type loader 1A, 1B of an example of construction vehicle as described above, its vehicle body is divided into the rear chassis 2 of rear section and the front chassis 3 of front part, and these chassis 2,3 can joltily be connected by center pin 4.
Be provided with for travelling the driving engine E driving vehicle body at the rear side of rear chassis 2, this driving engine E is connected with oil pressure pump 5.Again, rear chassis 2 is provided with operator's saddle 6, is thereunder provided with and turns to by control cock 7.On the other hand, front chassis 3 is provided with operating apparatus control cock 8.Like this, be configured with in wheel type loader 1A, the 1B turned to by control cock 7 and operating apparatus control cock 8, expecting pressure-gradient control valve 9 individually or with oil pressure pump 5, turn to become by any one structure in control cock 7 and operating apparatus control cock 8 and be configured integratedly.
When separate configurations pressure-gradient control valve 9, be necessary the housing that pressure-gradient control valve 9 is set in addition, and cause structure to increase to be arranged on rear chassis 2 or front chassis 3.Again, with oil pressure pump 5 formed carry out modularity integratedly time, the oil pressure pump 5 of this modularity becomes special product, thus the oil pressure pump of this oil pressure pump 5 by universal product can not be replaced, the poor availability of oil pressure pump 5.
Again, by turning to the maximum flow difference (generally speaking operating apparatus control cock 8 is relatively many) that can supply by control cock 7 and operating apparatus control cock 8, therefore in the pressure-gradient control valve 9 that the working oil coming from oil pressure pump 5 is carried out shunting, in order to reduce working oil by the loss of pressure (degradation of energy) time wherein, and the maximum flow being supplied to operating apparatus control cock 8 should be matched with, its spool is formed as than turning to the large diameter of the spool of control cock 7.Therefore, pressure-gradient control valve 9 and turn to the diameter of the spool of control cock 7 not identical, and as Fig. 5 (a) be shown in and make pressure-gradient control valve 9 and turn to in control cock 7 shape all-in-one-piece situation, when manufacturing when integrally carrying out modularity, have to be formed the spool bore of two different bores.Therefore, in the unit that pressure-gradient control valve 9 and turning to is formed as one with control cock 7, need, by the processing of these two spool bore different processing unit (plant), in the manufacture of foregoing units, to need more labour power.
As shown in Fig. 5 (b), when making pressure-gradient control valve 9 form as one with operating apparatus control cock 8, operating apparatus with the valve core diameter of control cock 8 and the valve core diameter of pressure-gradient control valve 9 roughly consistent, therefore above-mentioned carry out modularity like that and manufacture time, do not need more labour power.But in the structure shown here, pressure-gradient control valve 9 is arranged on front chassis 3, therefore connects the pipe arrangement of oil pressure pump 5 and pressure-gradient control valve 9 and be connected pressure-gradient control valve 9 and turn to two pipe arrangements leap center pins 4 of the pipe arrangement by control cock 7.These two pipe arrangements make high pressure and the pipe arrangement of the working oil of large discharge flowing, and the form being therefore difficult to cross over center pin 4 arranges.
Like this, when using pressure-gradient control valve 9, even if be arranged on any one position of vehicle body, various problems as described above can also all be there are.
Therefore, the object of this invention is to provide and can when not using pressure-gradient control valve preferentially come from the hydraulic pressure control device of the working oil of oil pressure pump to steering hardware supply and possess the vehicle for construction of this hydraulic pressure control device.
The means of dealing with problems:
Hydraulic pressure control device of the present invention possesses: the oil pressure pump connected with supplying working oil side by side to steering hardware and operating apparatus actr; Move by making spool control the direction of the working oil flowed in described steering hardware with this turn to by control cock; Described oil pressure pump is connected with tank by center position, deviation post controls the actr control cock in the direction of the working oil flowed in described operating apparatus actr; Control the inflow turning to the working oil by control cock described in being supplied to, and independently described turning to is kept certain inlet restriction formula compensator with the pressure reduction of the upstream side of control cock and the working oil in downstream with described turning to by the aperture of the spool of control cock; The inflow of the working oil of described actr control cock is supplied to control, and by the described pilot pressure turning to the pressure of the working oil in the downstream by control cock to be utilized as side, the pressure of the working oil of discharging from described oil pressure pump is utilized as the discharge formula compensator of the pilot pressure of the opposite side of revolting with the pilot pressure of described side.
According to the present invention, turn to the pressure reduction with the upstream side of control cock and the working oil in downstream by entry-type compensator compensates, the flow corresponding with the aperture turned to by control cock (displacement of spool) can be supplied to steering hardware with this.And, the pressure of the working oil in the downstream turned to by control cock is utilized as the pilot pressure of the side of discharge formula compensator, can be supplied to by discharge formula compensator the load pressure reflecting steering hardware in the flow of the working oil of operating apparatus actr with this.By means of this, the working oil needed for steering hardware can be guaranteed, and also can to operating apparatus actr supply working oil.
Again, by inlet porting throttle type compensator and these two control cock of the formula of discharge compensator, these two control cock can be designed by control cock and operating apparatus control cock matchingly with turning to respectively with this, thus can make to turn to control cock and the processing unit (plant) of inlet restriction formula compensator and the processing unit (plant) communization respectively of operating apparatus control cock and the formula of discharge compensator.Again, by arranging two control cock, these inlet restriction formula compensators can be connected with oil pressure pump side by side with discharge formula compensator with this.By means of this, can configure independently of each other and connect oil pressure pump and the pipe arrangement turned to by control cock and operating apparatus control cock.Therefore, can be used in to turn to by control cock and each middle inflow high pressure of operating apparatus control cock and the layout of each pipe arrangement of high-capacity working oil becomes simple.
In the present invention as stated above, preferably described discharge formula compensator is so that according to the pressure increase being supplied to the working oil in described steering hardware, mode from the working oil to the supply of described actr control cock that reduce the flow of works, and works in the mode making the pressure of the working oil of discharging from described oil pressure pump reach the pressure higher than the pressure of the working oil driven needed for described steering hardware.
According to the present invention, discharge formula compensator and reduce the flow flowed in actr control cock, thus make the pressure that the pressure of the working oil in inflow described inlet restriction formula compensator reaches higher than the operation pressure driven needed for described steering hardware.By means of this, the working oil of the pressure higher than the operation pressure driven needed for described steering hardware is easily made to flow into steering hardware side.Therefore, when driving steering hardware, the working oil coming from oil pressure pump can be made preferentially to flow in steering hardware with stable flow.That is, can working oil be made preferentially to flow in steering hardware with stable flow when not using pressure-gradient control valve.
In the present invention as stated above, the restriction between described actr control cock and described tank is preferably also possessed; Described oil pressure pump is the variable displacement pump regulating delivery flow according to the pressure of the working oil between described actr control cock and described restriction.
According to said structure, when driving steering hardware, by making working oil preferentially flow in steering hardware, be reduced by with this flow that discharge formula compensator flows into the working oil in restriction, thus at the pressure drop that the upstream side of restriction produces.Oil pressure pump increases discharge rate according to this pressure drop, the flow needed for the driving of steering hardware can be supplied to steering hardware from oil pressure pump.
In the present invention as stated above, preferably described inlet restriction formula compensator turns to described two guide oils being utilized as resistance mutually with the upstream side of control cock and the working oil in downstream; Also possess when the pressure of the guide oil of the working oil utilizing described downstream reaches authorized pressure, the guide oil of the working oil utilizing described downstream is expelled to the steering hardware side blowdown valve in tank.
According to said structure, can prevent pilot pressure from reaching more than authorized pressure.Namely, can prevent from flowing into turn to from inlet restriction formula compensator reaching more than authorized pressure with the pressure of the working oil control cock, the flow of described working fluid can be suppressed be less than the flow of specified value again, the working oil of desired amount can be made to flow in steering hardware.By means of this, can with the flows match flowed in inlet restriction formula compensator reduce its valve core diameter.Therefore, such as, the valve core diameter of inlet restriction formula compensator can be made and turn to match with the valve core diameter of control cock, even and if make inlet restriction formula compensator and turn to form one by control cock, also easily manufacture the unit of this integration.
Vehicle for construction of the present invention possesses any one hydraulic pressure control device above-mentioned.According to the present invention, the vehicle for construction possessing hydraulic pressure control device as described above can be realized.
The effect of invention:
According to the present invention, the working oil coming from oil pressure pump can be made preferentially to be supplied in steering hardware, connection oil pressure pump can be made to arrange simply with the pipe arrangement turned to by control cock and operating apparatus control cock.
Above-mentioned purpose of the present invention, other objects, feature and advantage, with reference on the basis of accompanying drawing, are understood by the detailed description of following preferred example.
Accompanying drawing explanation
Fig. 1 is the birds-eye view that the wheel type loader possessing hydraulic pressure control device of the present invention is shown;
Fig. 2 is the loop diagram of the oil hydraulic circuit that hydraulic pressure control device is shown;
Fig. 3 amplifies the loop diagram that the course changing control loop of hydraulic pressure control device is shown;
Fig. 4 amplifies the loop diagram that the operating apparatus control loop of hydraulic pressure control device is shown;
Fig. 5 is the birds-eye view that existing wheel type loader is shown, (a) in Fig. 5 is at the figure making pressure-gradient control valve with the wheel type loader 1A turned to when being formed integrally by control cock, and (b) in Fig. 5 is the figure of the wheel type loader when making pressure-gradient control valve and operating apparatus control cock form one.
Detailed description of the invention
[wheel type loader]
Fig. 1 is the birds-eye view that the wheel type loader 11 possessing hydraulic pressure control device 10 of the present invention is shown.The concept in the direction below illustrated is consistent towards the concept in direction during direct of travel with the chaufeur taken on wheel type loader 11.Wheel type loader 11 is one of so-called vehicle for construction, such as, be provided with scraper bowl 12 in its front, can get sand and rock etc. by this scraper bowl 12 shovel.In addition, the parts be installed on wheel type loader 11 are not limited to scraper bowl 12, also can be the accessory devices of fork and snow-removing device etc.Wheel type loader 11 possesses driving engine E and four wheel 13 on its vehicle body, is travelled by driving engine E rotary actuation wheel 13.
Again, the vehicle body of wheel type loader 11 is divided into the rear chassis 14 be configured on rear side of it and the front chassis 15 being configured in front side, and these two chassis 14,15 can joltily be connected by center pin 16.Again, between two chassis 14,15, erection has following two steering cylinders 18L, 18R(with reference to Fig. 2).Clip center pin as turning to two of actr steering cylinders 18L, 18R and be configured in the left and right sides respectively, a contraction is made with this by supplying working oil to two steering cylinders 18L, 18R, and make another stretch, front chassis 15 can be shaken relative to rear chassis 14 with this and change the direct of travel of wheel type loader 11.
Carry driving engine E at the rear side of the rear chassis 14 formed like this, be provided with operator's saddle 20 in front side.On front chassis 15, in the lateral direction across being arranged at intervals with two jibs 21 for making scraper bowl 12 be elevated.Each jib 21 can joltily be arranged on front chassis 15 in the vertical direction, is respectively arranged with jib cylinder 22 to them.By supplying working oil to this jib cylinder 22, with this, jib 21 is elevated.Again, front chassis 15 is provided with the pitching cylinder 23 for making scraper bowl 12 pitching in the vertical direction (fascinating).By supplying working oil to this pitching cylinder 23, make scraper bowl 12 pitching with this.
Like this, wheel type loader 11, by supplying working oil to steering cylinder 18L, 18R, jib cylinder 22 and pitching cylinder 23, changes direct of travel with this, scraper bowl 12 can be made again to be elevated or pitching.Wheel type loader 11 in order to these cylinders 18L, 18R, 22,23 supply working oils carry out driving and possess hydraulic pressure control device 10.
[hydraulic pressure control device]
Fig. 2 is the loop diagram of the oil hydraulic circuit that hydraulic pressure control device 10 is shown.Hydraulic pressure control device 10 possesses oil pressure pump 30, course changing control loop 31 and operating apparatus control loop 32 substantially.Oil pressure pump 30 is oil pressure pumps of so-called variable capacity type, and is connected with driving engine E.Oil pressure pump 30 is driven by driving engine E and discharges the working oil of high pressure.This oil pressure pump 30 is connected side by side with course changing control loop 31 and operating apparatus control loop 32, and the working oil coming from oil pressure pump 30 flows in course changing control loop 31 and operating apparatus control loop 32 concurrently.
[course changing control loop]
Fig. 3 amplifies the loop diagram that the course changing control loop 31 of hydraulic pressure control device 10 is shown.Below, be also described with reference to Fig. 2.Course changing control loop 31 substantially has inlet restriction formula compensator (meter-incompensator) 33 and turns to by control cock 34.Inlet restriction formula compensator 33 is flow-controlling gates, and primary side port 33a is connected with oil pressure pump 30, and secondary port 33b is connected by control cock 34 with turning to.Again, inlet restriction formula compensator 33 is formed with two pilot port 33c, 33d.The delivery pressure of secondary port 33b and the following delivery pressure turning to the second port 34b by control cock 34 is inputted, using each delivery pressure as the pilot pressure of side and opposite side in each pilot port 33c, 33d.The pilot pressure of side and opposite side acts on spool 33e with the form of mutually revolting, and the pilot pressure of side acts on spool 33e to the direction closed.Again, inlet restriction formula compensator 33 is provided with the pilot pressure of side mutinously to the spring member 33f that spool 33e exerts a force.The inlet restriction formula compensator 33 formed like this is according to the aperture of the pressure-difference valve core 33e of the pilot pressure of side and opposite side, and the working oil of the flow corresponding with this pressure reduction is flowed into and turns to in control cock 34, when this pressure reduction is equal with the force of spring member 33, the working oil of the flow preset is flowed into and turns to in control cock 34.
Turn to and be connected with steering cylinder 18L, 18R by control cock 34, and the direction of the working oil flowed in steering cylinder 18L, 18R can be switched.Turning to by control cock 34 is direction switch valves of five-port, first port 34a is connected with the secondary port 33b of inlet restriction formula compensator 33, second port 34b is connected with flow regulating valve 35 another pilot port 33d with inlet restriction formula compensator 33 by guide, and the 3rd port 34c is connected with tank 36.Again, the 4th port 34d and five-port 34e is connected with steering cylinder 18L, 18R.
Being switched the coupled condition of these five port 34a ~ 34e by the position that switches spool 34f with this, for spool 34f, the position of spool 34f can be switched with this by operating not shown steering handle (hereinafter referred to as " handle ").Turning to by control cock 34 is so-called neutral direction switch valves closing (centerclose) type, when spool 34f is positioned at center position 34A, first port 34a, the 4th port 34d and five-port 34e are cut-off, and the second port 34b and the 3rd port 34c is connected.By means of this, the guide oil being directed into the pilot port 33d of opposite side is expelled in tank 36, and the primary side port 33a of inlet restriction formula compensator 33 and secondary port 33b is closed.
When spool 34f is switched to the first deviation post 34B, the first port 34a is connected with five-port 34e by boiler check valve 38, and the 3rd port 34c is connected with the 4th port 34d.Now, be formed through spool 34f is moved with the structure of the aperture of this regulating spool 34f.By means of this, the steering cylinder 18R of opposite side stretches, and the steering cylinder 18L of side shrinks, thus front chassis 15 is turned to towards left direction.The delivery pressure of five-port 34e is inputted in the second port 34b at this moment.Therefore, inlet restriction formula compensator 33 makes to turn to in control cock 34 with turning to flow into the flow that the aperture of the spool 34f of control cock 34 is corresponding.
Again, when spool 34f is switched to the second deviation post 34C, the first port 34a is connected with the 4th port 34d by boiler check valve 38, and the 3rd port 34c is connected with five-port 34e.Now, be formed through spool 34f is moved with the structure of the aperture of this regulating spool 34f.By means of this, the steering cylinder 18L of side stretches, and the steering cylinder 18R of opposite side shrinks, thus front chassis 15 is turned to towards right direction.The delivery pressure of the 4th port 34d is inputted in the second port 34b at this moment.Therefore, when spool 34f is switched to the second deviation post 34C, inlet restriction formula compensator 33 makes to turn to in control cock 34 with turning to flow into the flow that the aperture of the spool 34f of control cock 34 is corresponding similarly.
Three blowdown valves 39 ~ 41 are also provided with in course changing control loop 31.First blowdown valve 39 and the second blowdown valve 40 are connected with the 4th port 34d and five-port 34e, when the 4th port 34d and five-port 34e and the pressure between steering cylinder 18L, 18R such as reach more than the pressure preset because of external force etc., working oil is expelled in tank 36.
Again, secondary blowdown valve 41 as the 3rd blowdown valve is connected with the pilot port 33d of the opposite side of inlet restriction formula compensator 33, when the pilot pressure of opposite side reaches more than the setting pressure preset, the guide oil of the pilot port 33d being directed into opposite side is expelled in tank 36.By means of this, when the pressure being directed into the working oil in steering cylinder 18L, 18R reaches more than authorized pressure, limit and flow into the flow of the working oil of steering cylinder 18L, 18R from secondary port 33b and prevent the pressure increase of this working oil, thus the pressure of this working oil is remained on setting pressure.
[operating apparatus control loop]
Fig. 4 amplifies the loop diagram that the operating apparatus control loop 32 of hydraulic pressure control device 10 is shown.Below, be also described with reference to Fig. 2.Operating apparatus control loop 32 has discharge formula compensator (bleed-offcompensator) 42, pitching control cock 43, jib control cock 44 and operating apparatus side restriction 45 substantially.Discharge formula compensator 42 is pressure-gradient control valves, and primary side port 42a is connected with oil pressure pump 30, and secondary port 42b is connected with pitching control cock 43.Again, discharge formula compensator 42 and be formed with two pilot port 42c, 42d.
The pilot port 42c of side is connected with primary side port 42a, inputs the inlet pressure of primary side port 42a wherein.The pilot port 42d of opposite side is connected with the electromagnetic switching valve 60 as switch unit.The pilot port 33d of the opposite side of electromagnetic switching valve 60 and primary side port 42a and inlet restriction formula compensator 33 is connected, and the pilot pressure inputed in the second pilot port 42d is switched to any one in the pilot pressure of the inlet pressure of primary side port 42a and the opposite side of inlet restriction formula compensator 33 according to instruction.The pilot pressure inputed to respectively in the pilot port 42c of side and opposite side, 42d acts on spool 42e in the mode of mutually revolting, and the pilot pressure of side acts on spool 42e to opening direction (specifically, by direction that the aperture of spool 42e is opened).Again, discharge formula compensator 42 is provided with the pilot pressure of side mutinously to the spring member 42f that spool 42 exerts a force.
The aperture of the discharge formula compensator 42 regulating spool 42e formed like this reaches the pressure corresponding with the force of spring member 42f with the pressure reduction of the pilot pressure of the side and opposite side that make the working oil coming from oil pressure pump 30.Specifically, discharging formula compensator 42 makes the pressure of the working oil in inflow inlet restriction formula compensator 33 and the formula of discharge compensator 42 reach than in order to drive the pressure that the operation pressure needed for steering cylinder 18R, 18L is high.Again, by the aperture of regulating spool 42e, discharge the flow of formula compensator 42 with this restricted passage.
Be connected with pitching cylinder 23 as a kind of pitching control cock 43 of actr by control cock, the direction flowing into the working oil pitching cylinder 23 from the formula of discharge compensator 42 can be switched.Pitching control cock 43 is direction switch valves of six ports, and the first port 43a is connected with the secondary port 42b of the formula of discharge compensator 42.Second port 43b is connected by the secondary port 42b of boiler check valve 47 with the formula of discharge compensator 42, and the 3rd port 43c is connected with tank 36.Again, the 4th port 43d is connected with jib control cock 44, and five-port 43e and the 6th port 43f is connected with pitching cylinder 23.
Switched the coupled condition of these six port 43a ~ 43f by the position that switches spool 43g with this, and the position of spool 43g can be switched by the pitch lever of operation setting in operator's saddle 20 (tiltlever) (not shown) with this.Pitching control cock 43 is direction switch valves of so-called open center type, and when spool 43g is positioned at center position 43A, the first port 43a and the 4th port 43d is connected, and other four ports 43b, 43c, 43e, 43f are cut-off.
When spool 43g is switched to the first deviation post 43B, the first port 43a and the 4th port 43d is cut off.On the contrary, the second port 43b is connected with the 6th port 43f, and the 3rd port 43c is connected with five-port 43e.By means of this, pitching cylinder 23 stretches, and scraper bowl 12 upwards rolls tiltedly.Again, when spool 43g is switched to the second deviation post 43C, the first port 43a and the 4th port 43d keeps cut-off state, and the second port 43b is connected with five-port 43e, and the 3rd port 43c is connected with the 6th port 43f.By means of this, pitching cylinder 23 shrinks, and scraper bowl 12 rolls downwards tiltedly.
The pitching control cock 43 formed like this can make scraper bowl 12 pitching in the vertical direction according to the operation of pitch lever.On the other hand, under the state not operating pitch lever, spool 43g is positioned on center position 43A, and the working oil therefore flowed in pitching control cock 43 is directed in jib control cock 44 through after the first port 43a and the 4th port 43d.
Be connected with jib cylinder 22 as the jib control cock 44 of actr with in control cock, the direction flowing into the working oil in jib cylinder 22 from the formula of discharge compensator 42 can be switched.Jib control cock 44 is direction switch valves of six ports, and the first port 44a is connected with the 4th port 43d of pitching by control cock 43.Second port 44b is connected by the secondary port 42b of boiler check valve 49 with the formula of discharge compensator 42, and the 3rd port 44c is connected with tank 36.Again, the 4th port 44d is connected with restriction 45, and five-port 44e and the 6th port 44f is connected with two jib cylinders 22.
By switching the position of spool 44g, switching the coupled condition of these six port 44a ~ 44f with this, and the position of spool 44g can be switched with this by the lifting bar of operation setting in operator's saddle 20 (not shown).Jib control cock 44 is direction switch valves of so-called open center type, and when spool 44g is positioned at center position 44A, the first port 44a and the 4th port 44d is connected, and other four ports 44b, 44c, 44e, 44f are cut-off.
When spool 44g is switched to the first deviation post 44B, the first port 44a and the 4th port 44d is cut off.On the contrary, the second port 44b is connected with the 6th port 44f, and the 3rd port 44c is connected with five-port 44e.By means of this, two jib cylinders 22 can be made to shrink, scraper bowl 12 is declined.Again, when spool 44g is switched to the second deviation post 44C, the first port 44a and the 4th port 44d keeps cut-off state, and the second port 44b is connected with five-port 44e, and the 3rd port 44c is connected with the 6th port 44f.By means of this, jib cylinder 22 can be made to stretch, make scraper bowl 12 increase.
In addition, jib control cock 44 can be switched to the 3rd deviation post 44D.When spool 44g is switched to the 3rd deviation post 44D, the first port 44a and the 4th port 44d keeps the state cut off, and the second port 44b, the 3rd port 44c, five-port 44e and the 6th port 44f are all connected with tank 36.By means of this, the jib confining force of cylinder 22 disappears, and can make jib 21 action freely.
The jib control cock 44 formed like this can make jib 21 be elevated in the vertical direction according to the operation of lifting bar.Under the state not operating lifting bar, spool 44g is positioned at center position 44A, and the working oil coming from pitching control cock 43 is directed in tank 36 by operating apparatus side restriction 45 through after jib control cock 44.Establishing operating apparatus side restriction 45 by being situated between, producing pressure with this upstream side in this operating apparatus side restriction 45.Be directed in oil pressure pump 30 using this pressure as command signal of verting, oil pressure pump 30, according to the discharge rate of the pressure change working oil of this command signal of verting, when verting the pressure increase of command signal, reduces discharge rate.By means of this, in operating apparatus control loop 32, realize negative control (negativecontrol).
Again, in operating apparatus control loop 32, four blowdown valves 50 ~ 53 are provided with.First blowdown valve 50 and the second blowdown valve 51 and pitching the five-port 43e of control cock 43 and the 6th port 43f are connected, when five-port 43d and the pressure between the 6th port 43f and scraper bowl cylinder 22 reach more than the pressure preset because of external force etc., the working oil flowed is expelled in tank 36 wherein.
Again, the 3rd blowdown valve 52 is connected side by side with operating apparatus side restriction 45, when the pressure flowing into the working oil in operating apparatus side restriction 45 reaches more than the pressure preset, is expelled in tank 36 by this working oil.By means of this, the pressure of the command signal that can prevent from verting reaches more than the pressure preset.
Again, the main blowdown valve 53 as the blowdown valve of the 4th is connected side by side with discharge formula compensator 42, when the discharge pressure of oil pressure pump 30 reaches more than the authorized pressure preset, is expelled in tank 36 by the working oil coming from oil pressure pump 30.By this main blowdown valve 53, can not only will flow into the pressure of the working oil in operating apparatus control loop 32 from oil pressure pump 30 but also the pressure of the working oil flowed in course changing control loop 31 also be remained on the pressure being less than authorized pressure.
[action of hydraulic pressure control device]
The action of hydraulic pressure control device 10 is described referring to Fig. 2.In hydraulic pressure control device 10, when driving engine E is driven, working oil discharged by oil pressure pump 30.Working oil flows in course changing control loop 31 and operating apparatus control loop 32.Under the situation of non-operating handle, turn to and be positioned on center position 34A by control cock 34.Therefore, cut off from turning to the inflow of control cock 34 to the working oil of steering cylinder 18L, 18R, the pilot port 33d of the opposite side of inlet restriction formula compensator 33 is connected with tank 36, is therefore closed between primary side port 33a and secondary port 33b.Therefore, working oil is stoped to flow into by control cock 34 from inlet restriction formula compensator 33 to turning to.
Now, when the pilot port 42d of the opposite side of the formula of discharge compensator 42 is connected by electromagnetic switching valve with the pilot port 33d of the opposite side of inlet restriction formula compensator 33, the pilot port 42d discharging the opposite side of formula compensator 42 is also connected with tank 36.Therefore, the spool 42e discharging formula compensator 42 moves to opening direction, and working oil is by discharge formula compensator 42.In such a case, pitching control cock 43 and jib control cock 44 are configured on center position 43A, 44A respectively, and pass pitching control cock 43 and jib control cock 44 with maintaining the original state through the working oil of discharge formula compensator 42, and flowed in tank 36 by operating apparatus side restriction 45.
In aforesaid situation, working oil does not flow in steering cylinder 18L, 18R, jib cylinder 22 and pitching cylinder 23.Therefore, the working oil coming from oil pressure pump 30 all flows in operating apparatus side restriction 45, and the pressure produced at the upstream side of operating apparatus side restriction 45 increases.Oil pressure pump 30 receives this pressure as command signal of verting, and reduces the pressure drop of discharge rate until command signal of verting to the pressure preset.The minimum flow rate preset is dropped to by means of this discharge rate.
Then, making at operating handle to turn to when being switched to the first deviation post 34B by control cock 34, being directed into steering cylinder 18L, 18R by control cock 34 from turning to.By means of this, the pilot pressure of opposite side rises, the spool 33e of inlet restriction formula compensator 33 to opening direction (specifically, direction by the aperture of spool 42e is closed) motion, thus from inlet restriction formula compensator 33 by turning to the working oil increase flowing into steering cylinder 18L, 18R by control cock 34.By means of this, steering cylinder 18R stretches, and steering cylinder 18L shrinks, and front chassis 15 left direction turns to.
Afterwards, inlet restriction formula compensator 33 makes the flow corresponding with the difference of pressure of the front and back pressure in the variable restrictor portion 37 turned to by control cock 34, namely turns to in control cock 34 with turning to flow into the working oil of the corresponding flow of the aperture of the spool 34f of control cock 34.That is, inlet restriction formula compensator 33 carries out pressure compensation to the flow flowing into steering cylinder 18L, 18R.Therefore, even if the pressure flowing into the working oil in inlet restriction formula compensator 33 changes, also can prevent the operation sense of handle from changing.
Making at operating handle to turn to when being switched to the second deviation post 34C by control cock 34, increasing by turning to the working oil with control cock 34 flows into steering cylinder 18L, 18R from inlet restriction formula compensator 33 similarly.By means of this, steering cylinder 18R shrinks, and steering cylinder 18L stretches, and front chassis 15 right direction turns to.Again, carry out the pressure compensation to the flow flowing into steering cylinder 18L, 18R by inlet restriction formula compensator 33, even if thus the pressure flowing into the working oil in inlet restriction formula compensator 33 change and also can prevent the operation sense of handle from changing.
Like this, by making working oil flow in steering cylinder 18L, 18R, the pilot pressure of the opposite side of discharge formula compensator 42 is made to increase with this.Along with this rising, discharge formula compensator 42 makes its spool 42e move to closing direction and reduce the aperture of spool 42e, thus make inflow discharge the pressure of the working oil in formula compensator 42 compared with the pressure of the working oil of inflow steering cylinder 18L, 18R, only improve the pressure corresponding with the force of spring member 42f, thus make the pressure of the working oil in inflow inlet restriction formula compensator 33 reach pressure higher than the operation pressure needed for driving steering cylinder 18L, 18R.Meanwhile, the flow by discharging the working oil of formula compensator 42 reduces.
Like this, reducing flow by improving the pressure of working oil, making the working oil of stable flow be easy to flow into steering cylinder 18L, 18R side from oil pressure pump 30 with this.That is, when driving steering cylinder 18L, 18R, the working oil coming from oil pressure pump 30 can be made preferentially to flow in steering cylinder 18L, 18R with stable flow.That is, can when making working oil preferentially flow in steering cylinder 18L, 18R with stably flow when existing such pressure-gradient control valve without the need to using.
Again, be reduced by the flow of the working oil of discharge formula compensator 42, reduce the flow of the upstream side flowing into operating apparatus side restriction 45 with this, thus at the pressure drop that the upstream side of aforementioned operating apparatus side restriction 45 produces.That is, the pressure of command signal of verting reduces, and the discharge rate of oil pressure pump 30 increases.By means of this, much more slightly from the working oil of the flow of the flow needed for pump delivery ratio steering control valve 34, thus working oil is stably supplied in steering cylinder 18L, 18R.
In addition, when in the pressure increase of working oil flowed in steering cylinder 18L, 18R, the pilot pressure of the opposite side of inlet restriction formula compensator 33 reaches more than setting pressure, secondary blowdown valve 41 is opened.By means of this, guide oil is expelled in tank 36, and the pilot pressure of aforementioned opposite side maintains the pressure being less than setting pressure.On the other hand, the pilot pressure of side continues along with the pressure increase of the working oil flowed in steering cylinder 18L, 18R to rise.By means of this, the spool 33e of inlet restriction formula compensator 33 moves to the direction closed, and the flow flowing into steering cylinder 18L, 18R is limited, thus prevents the pressure increase of aforementioned operation oil.That is, the top pressure flowing into the working oil of steering cylinder 18L, 18R reaches the authorized pressure corresponding with described setting pressure.
In addition, the pilot pressure of discharging the opposite side of formula compensator 42 also maintains setting pressure by secondary blowdown valve 41.Therefore, the spool 42e discharging formula compensator 42 moves to opening direction and increases the aperture of spool 42e, thus is increased by the flow of the working oil of discharge formula compensator 42.By means of this, increased by the flow of discharging the working oil of formula compensator 42, can will flow into the limitation of delivery of inlet restriction formula compensator 33 side from oil pressure pump 30 at the flow being less than regulation flow.
Like this, by limitation of delivery in inlet restriction formula compensator 33 will be flowed at the flow being less than regulation flow, the spool 33e of inlet restriction formula compensator 33 will be made to be formed as large footpath with this matchingly without the need to the discharge rate can discharged with oil pressure pump.That is, be formed as path while the spool 33e of inlet restriction formula compensator 33 and inflow flows match wherein can be made, the valve core diameter of inlet restriction formula compensator 33 can be made and turn to match with the valve core diameter of control cock 34.By means of this, easily manufacture inlet restriction formula compensator 33 and turn to control cock all-in-one-piece unit.
On the other hand, flow the flow identical with pitching control cock 43 and jib control cock 44 in discharge formula compensator 42, and therefore the valve core diameter of its valve core diameter and pitching control cock 43 and jib control cock 44 matches in most cases.Therefore, discharge formula compensator 42, pitching control cock 43 and jib control cock 44 all-in-one-piece unit is easily manufactured.
Again, when in order to the limitation of delivery flowing into inlet restriction formula compensator 33 side from oil pressure pump 30 is increased the aperture of the spool 42e of discharge formula compensator 42 at the flow being less than regulation flow, the pressure increase of the upstream side of operating apparatus side restriction 45.By means of this, the discharge rate of oil pressure pump 30 declines, thus supplies stable flow.
Here, when making the spool 43g of pitching control cock 43 be switched to the first deviation post 43B when operating pitch lever, working oil is stoped to flow into operating apparatus side restriction 45, the therefore pressure drop of the upstream side of operating apparatus side restriction 45.So the discharge rate of oil pressure pump 30 rises.The flow flowed in steering cylinder 18L, 18R maintains regulation flow, is therefore increased along with the discharge rate increase of oil pressure pump 30 by the flow of the working oil of discharge formula compensator 42.Flowed in pitching cylinder 23 by the working oil of this discharge formula compensator 42, stretch with this pitching cylinder 23, scraper bowl 12 upwards rolls tiltedly.
When making the spool 43g of pitching control cock 43 be switched to the second deviation post 43C operating pitch lever, except pitching cylinder 23 shrinks, carry out the action identical with the situation being switched to the first deviation post 43B.Again, when switching the position of spool 44g of jib control cock 44 operating lifting bar, except flexible actr is carry out the action identical with the situation of operation pitch lever except jib cylinder 22.
When non-operating handle, the working oil flowed into steering cylinder 18L, 18R from oil pressure pump 30 is as mentioned above cut off by inlet restriction formula compensator 33.Now, when operating pitch lever or lifting bar, coming from the working oil of oil pressure pump 30 all by discharge formula compensator 42, and flowing in pitching cylinder 23, jib cylinder 22 or this two cylinders 22,23.By means of this, compared with situation about pitch lever or lifting bar and handle being operated together, the working oil of large discharge can be made to flow in pitching cylinder 23 or jib cylinder 22, pitching cylinder 23 or jib cylinder 22 can be made with speed motion faster.
Like this when driving pitching cylinder 23 or jib with cylinder 22, when the pressure flowing into the working oil in discharge formula compensator 42 reaches more than authorized pressure, the working oil that main blowdown valve 53 makes inflow discharge in formula compensator 42 is expelled in tank 36.By means of this, the top pressure of the working oil in inflow pitching cylinder 23 or jib cylinder 22 can be made to reach authorized pressure.Therefore, can be set in respectively in operating apparatus control loop 32 working oil of flowing top pressure and in course changing control loop 31 top pressure of the working oil of flowing.
Below illustrate in the hydraulic pressure control device 10 worked like this, the pilot pressure inputing to the pilot port 42d of the opposite side of discharge formula compensator 42 is switched to the situation of inlet pressure, the i.e. pump pressure of primary side port 42a by electromagnetic switching valve 60.When switching pilot pressure, identical load acts on the both ends of the spool 42e of discharge formula compensator 42, discharges the spool 42e of formula compensator 42 and is independently maintained in its closed position the operation of handle, pitch lever and lifting bar.By means of this, the working oil of discharging from pump 30 is back to tank 36 by main blowdown valve 53.By means of this, the discharge pressure of pump 30 rises to the setting pressure preset of main blowdown valve 53, can improve the load of driving engine E.Again, in hydraulic pressure control device 10, even if when like this forcibly improving the load of driving engine E, also the working oil of stable flow can be made to flow in steering cylinder 18R, 18L by inlet restriction formula compensator 33 when operating handle.Therefore, even if when forcibly improving the load of driving engine E, also can at random drive steering cylinder 18R, 18L.
That is, by electromagnetic switching valve 60, pump pressure is inputed in the pilot port 42d of opposite side of discharge formula compensator 42, the load of driving engine E can be improved with this forcibly.Again, inlet restriction formula compensator 33 and the formula of discharge compensator 42 are formed as the structure of separate component, even if therefore when improving the load of driving engine E forcibly, steering cylinder 18L, 18R also can be made to work.
In this example, describe hydraulic pressure control device 10,100 and be mounted in situation on wheel type loader 11, but also can be bulldozer (bulldozer) etc., as long as vehicle for construction.Again, the actr driven by hydraulic pressure control device 10,100 is jib cylinder 22 and these two actrs of pitching cylinder 23, but also can be merely the actr of any one, or also can be possess the actr of more than three, and drives these actrs.Again, the kind of steering hardware and actr is also not limited to cylinder, also can be hydraulic motor.
By above-mentioned explanation, those skilled in the art understand more improvement of the present invention and other examples etc.Therefore, above-mentioned explanation only should illustratively be explained, is to implement to provide for the purpose of most preferred form of the present invention to instruct to those skilled in the art.Without departing from the spirit of the invention within the scope, the particular content of its structure and/or function can be changed in fact.
Nomenclature:
10 hydraulic pressure control devices;
11 wheel type loaders;
18L, 18R steering cylinder;
22 jib cylinders;
23 pitching cylinders;
30 oil pressure pumps;
33 inlet restriction formula compensators;
34 turn to by control cock;
36 steering hardware side tanks;
41 secondary blowdown valves;
42 discharge formula compensator;
43 pitching control cock;
44 jib control cock;
45 operating apparatus restriction;
48 operating apparatus side tanks;
53 main blowdown valves.
Claims (5)
1. a hydraulic pressure control device, possesses:
To the oil pressure pump that steering hardware and operating apparatus actr connect with supplying working oil side by side;
Move by making spool control the direction of the working oil flowed in described steering hardware with this turn to by control cock;
Described oil pressure pump is connected with tank by center position, deviation post controls the actr control cock in the direction of the working oil flowed in described operating apparatus actr;
Control the inflow turning to the working oil by control cock described in being supplied to, and independently described turning to is kept certain inlet restriction formula compensator with the pressure reduction of the upstream side of control cock and the working oil in downstream with described turning to by the aperture of the spool of control cock; With
Without the need to supplying working oil by control cock and the inflow controlling to be supplied to the working oil of described actr control cock to described turning to, and by the described pilot pressure turning to the pressure of the working oil in the downstream by control cock to be utilized as side, the pressure of the working oil of discharging from described oil pressure pump is utilized as the discharge formula compensator of the pilot pressure of the opposite side of revolting with the pilot pressure of described side.
2. hydraulic pressure control device according to claim 1, it is characterized in that, described discharge formula compensator so that according to the pressure increase being supplied to the working oil in described steering hardware, mode from the working oil to the supply of described actr control cock that reduce the flow of works, and works in the mode making the pressure of the working oil of discharging from described oil pressure pump reach the pressure higher than the pressure of the working oil driven needed for described steering hardware.
3. hydraulic pressure control device according to claim 1, is characterized in that,
Also possesses the restriction between described actr control cock and described tank;
Described oil pressure pump is the variable displacement pump regulating delivery flow according to the pressure of the working oil between described actr control cock and described restriction.
4. hydraulic pressure control device according to claim 1, is characterized in that,
Described inlet restriction formula compensator turns to described two guide oils being utilized as resistance mutually with the upstream side of control cock and the working oil in downstream;
Also possess when the pressure of the guide oil of the working oil utilizing described downstream reaches authorized pressure, the guide oil of the working oil utilizing described downstream is expelled to the steering hardware side blowdown valve in tank.
5. a vehicle for construction, possesses the hydraulic pressure control device in Claims 1-4 described in any one.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2011269293A JP6001846B2 (en) | 2011-12-08 | 2011-12-08 | Hydraulic control device and construction machine including the same |
| JP2011-269293 | 2011-12-08 | ||
| PCT/JP2012/007710 WO2013084456A1 (en) | 2011-12-08 | 2012-11-30 | Hydraulic control device and construction machine with same |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103917431A CN103917431A (en) | 2014-07-09 |
| CN103917431B true CN103917431B (en) | 2016-03-30 |
Family
ID=48573847
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201280054904.1A Active CN103917431B (en) | 2011-12-08 | 2012-11-30 | Hydraulic pressure control device and possess the vehicle for construction of this hydraulic pressure control device |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US9821840B2 (en) |
| JP (1) | JP6001846B2 (en) |
| CN (1) | CN103917431B (en) |
| IN (1) | IN2014CN04500A (en) |
| WO (1) | WO2013084456A1 (en) |
Families Citing this family (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5809549B2 (en) * | 2011-12-08 | 2015-11-11 | 株式会社Kcm | Hydraulic drive |
| JP6134263B2 (en) * | 2013-12-27 | 2017-05-24 | 株式会社Kcm | Hydraulic drive system |
| JP6621130B2 (en) * | 2015-02-06 | 2019-12-18 | キャタピラー エス エー アール エル | Hydraulic actuator control circuit |
| CN105201944B (en) * | 2015-09-25 | 2017-10-03 | 广西柳工机械股份有限公司 | Flux amplification valve and steering hydraulic system |
| JP6730798B2 (en) * | 2015-11-17 | 2020-07-29 | ナブテスコ株式会社 | Hydraulic drive |
| US20180372088A1 (en) * | 2015-12-16 | 2018-12-27 | Walvoil S.P.A. | Hydraulic valve device with multiple working sections with pump control system |
| CN106948404A (en) * | 2017-04-12 | 2017-07-14 | 管中林 | One kind has multi-functional walking excavating machine |
| JP6858723B2 (en) * | 2018-03-28 | 2021-04-14 | 日立建機株式会社 | Wheel loader |
| CN108953261B (en) * | 2018-09-11 | 2023-07-11 | 圣邦集团有限公司 | Hydraulic control system and control method for crawler-type harvester |
| JP7106466B2 (en) * | 2019-02-05 | 2022-07-26 | 株式会社クボタ | work vehicle |
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| CN1984807A (en) * | 2004-07-13 | 2007-06-20 | 日立建机株式会社 | Hydraulic drive device for working vehicle |
| CN101489853A (en) * | 2006-12-21 | 2009-07-22 | 日立建机株式会社 | Steering system for working vehicle |
| CN101516715A (en) * | 2006-12-26 | 2009-08-26 | 日立建机株式会社 | Steering system for working vehicle |
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| JPS5970245A (en) * | 1982-10-13 | 1984-04-20 | Daikin Ind Ltd | Oil pressure circuit for car |
| US4463557A (en) * | 1983-08-12 | 1984-08-07 | Deere & Company | Open center hydraulic system |
| JP2688493B2 (en) * | 1988-07-04 | 1997-12-10 | 東芝機械株式会社 | Hydraulic circuit |
| JPH02107802A (en) * | 1988-08-31 | 1990-04-19 | Hitachi Constr Mach Co Ltd | Hydraulic driving device |
| JPH02193769A (en) * | 1989-01-21 | 1990-07-31 | Yutani Heavy Ind Ltd | Steering operating sensitivity change-over device |
| JPH05164106A (en) * | 1991-12-06 | 1993-06-29 | Iseki & Co Ltd | Hydraulic circuit for steering combine harvester or the like |
| DE4304376C2 (en) * | 1993-02-13 | 1997-08-07 | Hydraulik Nord Gmbh | Load measuring steering system |
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| JP2006290236A (en) * | 2005-04-13 | 2006-10-26 | Hitachi Constr Mach Co Ltd | Hydraulic drive device |
| EP2098437B1 (en) * | 2006-12-26 | 2017-11-15 | KCM Corporation | Steering system for working vehicle |
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2011
- 2011-12-08 JP JP2011269293A patent/JP6001846B2/en active Active
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2012
- 2012-11-30 US US14/364,018 patent/US9821840B2/en active Active
- 2012-11-30 IN IN4500CHN2014 patent/IN2014CN04500A/en unknown
- 2012-11-30 WO PCT/JP2012/007710 patent/WO2013084456A1/en active Application Filing
- 2012-11-30 CN CN201280054904.1A patent/CN103917431B/en active Active
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1984807A (en) * | 2004-07-13 | 2007-06-20 | 日立建机株式会社 | Hydraulic drive device for working vehicle |
| CN101489853A (en) * | 2006-12-21 | 2009-07-22 | 日立建机株式会社 | Steering system for working vehicle |
| CN101516715A (en) * | 2006-12-26 | 2009-08-26 | 日立建机株式会社 | Steering system for working vehicle |
Also Published As
| Publication number | Publication date |
|---|---|
| IN2014CN04500A (en) | 2015-09-11 |
| WO2013084456A1 (en) | 2013-06-13 |
| CN103917431A (en) | 2014-07-09 |
| JP6001846B2 (en) | 2016-10-05 |
| US20140318116A1 (en) | 2014-10-30 |
| US9821840B2 (en) | 2017-11-21 |
| JP2013119358A (en) | 2013-06-17 |
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Effective date of registration: 20191118 Address after: Kobe City, Hyogo Prefecture, Japan Co-patentee after: Hitach Construction Machinery Co., Ltd. Patentee after: Kawasaki Jukgyo K. K. Address before: Kobe City, Hyogo Prefecture, Japan Co-patentee before: KCM K. K. Patentee before: Kawasaki Jukgyo K. K. |
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| TR01 | Transfer of patent right |